JPS6260581B2 - - Google Patents

Info

Publication number
JPS6260581B2
JPS6260581B2 JP56115023A JP11502381A JPS6260581B2 JP S6260581 B2 JPS6260581 B2 JP S6260581B2 JP 56115023 A JP56115023 A JP 56115023A JP 11502381 A JP11502381 A JP 11502381A JP S6260581 B2 JPS6260581 B2 JP S6260581B2
Authority
JP
Japan
Prior art keywords
bellows
sealing
sealing device
mechanical
curvature
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
JP56115023A
Other languages
Japanese (ja)
Other versions
JPS5743060A (en
Inventor
Ratsukusufuoodo Jofurii
Ansonii Meisamu Guranto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Crane Packing Ltd
Original Assignee
Crane Packing Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Crane Packing Ltd filed Critical Crane Packing Ltd
Publication of JPS5743060A publication Critical patent/JPS5743060A/en
Publication of JPS6260581B2 publication Critical patent/JPS6260581B2/ja
Granted legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/36—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member connected by a diaphragm or bellow to the other member
    • F16J15/363—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member connected by a diaphragm or bellow to the other member the diaphragm or bellow being made of metal
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/922—Bonding or joining for manufacture of seal
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/925—Snap fit feature for mounting or assembly of seal

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Sealing (AREA)
  • Diaphragms And Bellows (AREA)

Description

【発明の詳細な説明】 本発明は機械的面密封装置に関し、特に曲げや
すく弾力のある蛇腹を有する機械的面密封装置に
関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to mechanical surface sealing devices, and more particularly to mechanical surface sealing devices having flexible and resilient bellows.

相対的に回転可能な一対の機械構成要素の間を
密封するための機械的面密封装置の一つの形式
は、該要素の一つに液密態様で固着された第一の
密封部材と第一の密封面部材の向き合つた密封面
の方に押し付けられている密封面を有する第二の
密封面部材とよりなり、第二の密封面部材は曲げ
やすく弾力のある蛇腹によつて別の構成要素に固
着されている。この形の密封装置では蛇腹は第二
の密封面部材とその連合する構成要素との間の密
封装置としての役をし又第二の密封面部材を第一
の密封面部材と密封係合させるのに必要な軸方向
荷重を適用するのに役立つ。 One type of mechanical surface sealing device for sealing between a pair of relatively rotatable mechanical components includes a first sealing member affixed in a fluid-tight manner to one of the components; a second sealing face member having a sealing surface pressed toward the opposite sealing face of the sealing face member, the second sealing face member having a separate configuration by a pliable resilient bellows. Attached to the element. In this type of seal, the bellows serves as a seal between the second seal face member and its associated component and brings the second seal face member into sealing engagement with the first seal face member. This helps in applying the necessary axial loads.

運転中に蛇腹はその壁の内外面に圧力差を受
け、そのために蛇腹は密封面部材に適当な荷重を
加えることができなければならないだけでなく、
それが受ける圧力差によく耐えることができなけ
ればならない。さらに密封面部材は損耗するの
で、蛇腹は延びることができ且つ密封装置の寿命
期間にわたつてある限界内の荷重を与えるもので
なければならない。従つて、蛇腹は圧力差に耐え
るために充分な強さと厚みのある材料で作られな
ければならないし、同時に損耗のために必要な軸
方向の動きができるために充分に曲げやすくなけ
ればならず、同時に必要な軸方向の推力を持つて
いなければならない。 During operation, the bellows is subjected to pressure differences between the inner and outer surfaces of its walls, so that the bellows must not only be able to apply a suitable load to the sealing face member;
It must be able to withstand well the pressure differences to which it is subjected. Furthermore, since the sealing face member wears, the bellows must be able to extend and carry loads within certain limits over the life of the sealing device. Therefore, the bellows must be made of a material of sufficient strength and thickness to withstand the pressure differential, while at the same time being sufficiently pliable to allow the necessary axial movement for wear and tear. , and at the same time must have the necessary axial thrust.

これを達成する一方法は、復数個の環状の円板
を溶接することによつて蛇腹を作ることであり、
一連のひだ（convolution）を作るために対の円
板を一つおきにそれらの内径と外径のところで一
緒にくつつける。この型の蛇腹を造るのは、しか
し乍ら時間と費用のかかる方法である。さらに、
溶接蛇腹装置の「水圧均衡直径（hydraulic
balance diameter）」は、その壁の内外面の圧力
差によつて変わり、蛇腹は、密封面部材の全体的
な設計はそれが受けるあらゆる圧力差で満足に作
用する密封装置を提供するために、この変化に適
応させなければならない。 One way to accomplish this is to make the bellows by welding together several annular discs,
Alternate pairs of discs are glued together at their inner and outer diameters to create a series of convolutions. Making this type of bellows, however, is a time consuming and expensive process. moreover,
Hydraulic balance diameter (hydraulic) of welded bellows equipment
The overall design of the sealing face member is such that the overall design of the sealing face member provides a sealing device that operates satisfactorily at any pressure difference to which it is subjected. We must adapt to this change.

蛇腹を作る一層安価な方法は、壁の肉の薄い管
のひだを作ることである。この型の蛇腹（以下一
体形成蛇腹と称する）は、「水圧均衡直径」が実
質的に一定であり、その結果その蛇腹は、密封面
部材の設計上の制限が溶接蛇腹のそれに比べて大
きくないという利点がある。残念乍ら、一般的に
一体形成蛇腹では、曲がりやすさと要求される耐
圧性とは相容れない。結果として、受け入れるこ
とのできないほど長くなく、必要な表面荷重を与
えるに充分なほどに曲がりやすい、相応に高圧性
能を有する一体形成蛇腹を作ることはできないで
きた。 A cheaper method of making bellows is to make thin tube pleats of wall flesh. This type of bellows (hereinafter referred to as an integrally formed bellows) has a substantially constant "hydraulic balance diameter" so that the design limitations of the sealing face member are no greater than those of welded bellows. There is an advantage. Unfortunately, integrally formed bellows are generally not compatible with ease of bending and required pressure resistance. As a result, it has not been possible to create a one-piece bellows that is not unacceptably long and flexible enough to provide the necessary surface loads, and that has correspondingly high pressure capabilities.

作つて、本発明の目的は、一体形成蛇腹であつ
て、なお且つ曲がり易さと耐圧性とを両立させ得
る機械的面密封装置を提供することにある。本発
明の一実施態様によれば、相対的に回転可能な一
対の機械構成要素の間に密封を形成し、使用する
際に圧力差を受ける機械的密封装置において、面
密封装置は、該構成要素の一方に液密態様で固着
されていて密封面を有する第１密封面部材と第１
密封面部材の密封面に押し付けられている密封面
を有する第２の密封面部材とよりなり、第２密封
面部材は、他の構成要素に第２密封面部材を密封
させる役目をする曲がりやすく弾力のある一体形
成蛇腹（以下に詳述）が、つばを介して他の構成
要素に固着されており、該蛇腹は複数のひだを有
し、面密封装置の高圧側の方に向いているひだの
山は面密封装置の低圧側の方を向いているひだの
山よりも曲率半径が大きく形成されている。 An object of the present invention is to provide a mechanical surface sealing device which is an integrally formed bellows and which is both flexible and pressure resistant. According to one embodiment of the present invention, in a mechanical sealing device that forms a seal between a pair of relatively rotatable mechanical components and is subjected to a pressure differential in use, the face sealing device a first sealing surface member affixed in a liquid-tight manner to one of the elements and having a sealing surface;
a second sealing face member having a sealing surface pressed against the sealing face of the sealing face member, the second sealing face member being flexible and serving to seal the second sealing face member to other components; A resilient, integrally formed bellows (detailed below) is secured to the other components via a collar, the bellows having a plurality of pleats and oriented toward the high pressure side of the face seal. The ridges of the pleats are formed to have a larger radius of curvature than the ridges of the pleats facing toward the low pressure side of the surface sealing device.

一般に大きな曲率半径と小さな曲率半径でもつ
て交互に折り返して蛇腹状に形成させたものは、
大きな曲率半径の側から小さな曲率半径の側に押
した場合の方がその反対に押した場合よりも変形
しにくい。 Generally, a bellows-like shape is formed by folding back alternately with a large radius of curvature and a small radius of curvature.
When pushed from the side with a large radius of curvature to the side with a small radius of curvature, it is less likely to deform than when pushed in the opposite direction.

又大きな曲率半径でもつてＵ字型に折り返した
方が小さな曲率半径で折り返した場合に比べて、
より容易に即ちより小さな力で両直線部分を押し
拡げたり押し狭めたりすることが出来る。 Also, it is better to fold the U-shape even with a large radius of curvature than to fold it back with a small radius of curvature.
Both straight portions can be expanded or narrowed more easily, that is, with less force.

このため、本発明による一体形成蛇腹のように
曲率半径の大きいひだの山と曲率半径の小さいひ
だの山とを交互に配設して、大きいひだの山を高
圧側に向けた場合には、従来の一体形成蛇腹に比
べて、また勿論その反対の場合に比べて、高圧側
から低圧側への押圧力が一体形成蛇腹を低圧側に
押し凹まそうとする力が低減することになる。も
つて、同じ強さの素材を用いた場合には、本発明
の一体形成蛇腹はより大きな圧力に耐えることが
できるものである、 また上記の如く、損耗をカバーするために必要
な形成蛇腹の曲がり易さ、即ち軸方向への伸長し
易さが必要かつ充分に得られるものである。 For this reason, when the integrally formed bellows according to the present invention alternately arranges fold peaks with a large radius of curvature and fold peaks with a small radius of curvature, with the large fold peaks facing the high pressure side, Compared to conventional integrally formed bellows, and of course, compared to the reverse, the pressing force from the high pressure side to the low pressure side tends to push the integrally formed bellows toward the low pressure side. Therefore, if materials of the same strength are used, the integrally formed bellows of the present invention can withstand greater pressure, and as mentioned above, the formed bellows required to cover wear and tear is Ease of bending, that is, ease of stretching in the axial direction, is necessary and sufficient.

従つて、本発明による一体形成蛇腹を採用する
ことによつて、蛇腹は従来の対称的な構造の一体
形成蛇腹よりも薄い材料で作ることができ、それ
は同じ圧力差に耐えるでろう。その結果、ある与
えられた圧力差のために一層曲がりやすい蛇腹を
作ることが本発明によつて可能であり、その結
果、機械的面密封装置にとつて受け入れることの
できる容積、圧力能及び曲がりやすさをもつた一
体形成蛇腹を作ることができる。反対に、従来の
対称的に形作られた蛇腹の曲がりやすさと同じ曲
がりやすさを有する本発明による蛇腹はより大き
な圧力能を有する。 Therefore, by employing a one-piece bellows according to the present invention, the bellows can be made of thinner material than a conventional symmetrically constructed one-piece bellows, and it will withstand the same pressure differential. As a result, it is possible with the present invention to create a bellows that is more flexible for a given pressure difference, resulting in an acceptable volume, pressure capacity and bending for a mechanical surface sealing device. It is possible to easily make an integrally formed bellows. On the contrary, the bellows according to the invention having the same bendability as that of a conventional symmetrically shaped bellows has a greater pressure capacity.

本発明によつて設計された蛇腹の曲がりやすさ
もしくは圧力能における重要な改善は蛇腹の高圧
側に向いているひだの山の曲率半径の低圧側に向
いている山の曲率半径に対する比を３：２又はそ
れ以上にすることによつて達成される。しかし乍
ら、２：１から６：１の比を用いることが好まし
い。 A significant improvement in the bendability or pressure capacity of the bellows designed in accordance with the present invention is that the ratio of the radius of curvature of the ridges of the pleats facing the high pressure side of the bellows to the radius of curvature of the crests of the pleats facing the low pressure side of the bellows is increased by 3. :2 or more. However, it is preferred to use a ratio of 2:1 to 6:1.

本発明を図に基づいて詳細に説明する。 The present invention will be explained in detail based on the drawings.

例えばポンプ装置の回転軸１０とハウジング１
１の間の機械的面密封装置は、ハウジング１１の
段部に保持された第一の環状密封部材即ち台座１
２を有し、台座１２の凹部にエラストマーのＯ−
リング１３によつてハウジングに密封されてい
る。環状の密封面部材１５の密封表面１４は、ぐ
るりに間隔をおいて設けた一連のグラブねじ２３
によつてあるいは他の適当な固定手段によつて、
軸１０上に設けたつば１７に固着され、そこにＯ
−リング１８によつて密封された金属一体形成蛇
腹１６によつて台座１２と密封接触を維持してい
る。密封面部材１５は蛇腹１６の端にプレスばめ
され、エラストマーのＯ−リング２０は、蛇腹１
６の一番外側のひだの中に保持され、面部材１５
はその間に液の漏れを防ぐ密封を作る役目をす
る。蛇腹の他の端１６はつば１７に溶接されてい
るが、例えば、すえ込みあるいはろう付けのよう
な液の漏れない他の接合手段によつてつばに固着
してよい。 For example, the rotating shaft 10 and housing 1 of a pump device
1 includes a first annular sealing member or pedestal 1 held in the step of the housing 11;
2, and an elastomer O-
It is sealed to the housing by a ring 13. The sealing surface 14 of the annular sealing face member 15 includes a series of grub screws 23 spaced around the circumference.
or by other suitable fixing means,
It is fixed to the collar 17 provided on the shaft 10, and O
- maintained in sealed contact with the base 12 by a metal integral bellows 16 sealed by a ring 18; A sealing face member 15 is press fit to the end of the bellows 16 and an elastomeric O-ring 20 is attached to the end of the bellows 16.
6 and held within the outermost folds of the face member 15
serves to create a seal between them to prevent liquid leakage. The other end 16 of the bellows is welded to the collar 17, but may be secured to the collar by other leaktight joining means, such as swaging or brazing.

金属製蛇腹１６は一連のひだよりなり、軸１０
から遠い方のひだの山２１の曲率半径は軸１０の
方に向かうひだの山２２の曲率半径よりも大き
く、その比は４：１である。 The metal bellows 16 consists of a series of pleats, and the shaft 10
The radius of curvature of the ridges 21 of the pleats facing away from the axis 10 is greater than the radius of curvature of the ridges 22 of the pleats facing towards the axis 10, the ratio being 4:1.

上記の密封装置は、面部材１５の密封表面１４
が台座１２と密封係合しているように、蛇腹１６
が押し縮められそして台座１２の方に面部材１５
を予荷重するように組立てる。 The above-described sealing device includes a sealing surface 14 of a face member 15.
The bellows 16 is in sealing engagement with the base 12.
is compressed and the surface member 15 is moved toward the pedestal 12.
Assemble to preload.

運転中、密封装置はその面の前後に圧力差を受
け、蛇腹の内側に比べて高圧域Ｐは蛇腹１６の外
側にある。 During operation, the sealing device experiences a pressure difference across its face, with the high pressure area P being on the outside of the bellows 16 compared to the inside of the bellows.

蛇腹１６の内外面の圧力差は、その外側面即ち
高圧域Ｐの面の全域に等しく加わり、従つて、実
質的に非曲率部分２４にも等しく加わることにな
り、その結果としてこの圧力差はそれぞれの非曲
率部分２４を矢印で示す反対方向即ち軸方向に圧
力差に比例して押し拡げる力を生ずる。この軸方
向の力は軸方向に圧縮されている蛇腹１６によつ
て密封面部材に加えられる初期の力を強める。運
転状態で加えられるこの附加的な力のために、広
い範囲の運転状態の下で、台座１２と密封面部材
１５の間に加えられる荷重は普通の状態において
効果的な密封をつくるために必要な荷重よりもわ
ずかに大きい。この方法によつて密封面部材１５
の損耗が最小になる。 The pressure difference between the inner and outer surfaces of the bellows 16 is equally applied to the entire outer surface of the bellows 16, that is, the surface of the high pressure region P, and is therefore equally applied to the non-curvature portion 24. As a result, this pressure difference is A force is generated that pushes each non-curved portion 24 apart in the opposite direction, ie, the axial direction, as indicated by the arrow, in proportion to the pressure difference. This axial force intensifies the initial force exerted on the sealing face member by the axially compressed bellows 16. Because of this additional force applied during operating conditions, under a wide range of operating conditions, the load applied between the pedestal 12 and the sealing face member 15 is necessary to create an effective seal under normal conditions. slightly larger than the normal load. By this method, the sealing surface member 15
wear and tear is minimized.

この運転の型は、それ自体は新しいものではな
い。本発明は蛇腹１６の新規なひだにあり、その
ひだは蛇腹の特性を一層大きく制御することを可
能にする。例えば、蛇腹が受ける圧力差に耐える
ためには、蛇腹は、つぶれないで圧力に耐えるた
めに充分な強度と規格の材料で作らなければなら
ない。ここで特許請求されている構造は、蛇腹を
同じ圧力差に耐える従来の対称的な設計の蛇腹に
必要であるよりも軽い規格の材料で作ることを可
能にする。軽い規格の材料を使用すると蛇腹の軸
方向の曲げやすさが増し、本発明の蛇腹を使うと
蛇腹は最初により大きな程度で圧縮され、それに
よつて、その耐用年限中ずつと、面部材１５によ
り均一な予荷重を加える。 This type of driving is not new per se. The invention resides in a novel corrugation of the bellows 16, which corrugations allow greater control over the characteristics of the bellows. For example, in order for a bellows to withstand the pressure differentials it is subjected to, the bellows must be made of a material of sufficient strength and specification to withstand the pressure without collapsing. The structure claimed herein allows the bellows to be made of a lighter grade material than is required for a conventional symmetrically designed bellows to withstand the same pressure differential. The use of lighter grade materials increases the axial bendability of the bellows, and with the bellows of the invention the bellows is initially compressed to a greater extent, thereby allowing the surface member 15 to Apply uniform preload.

以下の実施例は蛇腹の性能の改良を示し、その
蛇腹は本発明によつて達成されたものである。 The following examples demonstrate improvements in the performance of bellows, which were achieved in accordance with the present invention.

実施例 三個の蛇腹Ａ，Ｂ及びＣを同じ材料で作つた。
各部品は外径66.58mm、内径53.42mm、壁肉0.18mm
である。三個の部品はすべて平らな丸味のついた
ひだがついており、ひだの壁は図に示すように、
蛇腹の軸線に実質的に直角である。EXAMPLE Three bellows A, B and C were made of the same material.
Each part has an outer diameter of 66.58mm, an inner diameter of 53.42mm, and a wall thickness of 0.18mm.
It is. All three parts have flat, rounded pleats, and the walls of the pleats are as shown in the figure.
substantially perpendicular to the axis of the bellows.

蛇腹Ａは従来の対称的な構造であり、ひだの内
側の山と外側の山の曲率半径とは等しく、ひだの
ピツチは7.21mmである。蛇腹Ｂ及びＣは本発明に
従つて作り、ひだの外側の山の曲率半径は内側の
山のそれの２倍であり、ひだのピツチは蛇腹Ｂで
は5.67mm、蛇腹Ｃでは7.1mmである。 Bellows A has a conventional symmetrical structure, the radius of curvature of the inner and outer ridges of the pleats is equal, and the pitch of the pleats is 7.21 mm. Bellows B and C are made according to the invention, the radius of curvature of the outer peaks of the pleats being twice that of the inner peaks, and the pitch of the pleats being 5.67 mm for bellows B and 7.1 mm for bellows C.

それらの蛇腹を300ニユートンの初期の軸方向
の力を加えるために制御された軸方向の移動でも
つて予め圧縮すると、 蛇腹Ａ及びＢは、同じような圧力性能を示した
が、蛇腹Ｂは蛇腹Ａに比べて曲がりやすさにおい
て45％の改良を示した。又蛇腹Ａ及びＣは同じよ
うな曲がりやすさを示したが蛇腹Ｃは蛇腹Ａより
も圧力性能において31％の改良を示した。 When the bellows were precompressed with controlled axial movement to apply an initial axial force of 300 Newtons, bellows A and B showed similar pressure performance, but bellows B Compared to A, it showed a 45% improvement in bendability. Also, although bellows A and C exhibited similar bendability, bellows C showed a 31% improvement in pressure performance over bellow A.

上記の実施例に示されるように、本発明に従つ
て使われる蛇腹は、対称的な構造の同じような従
来の蛇腹に比べて、改良された曲がりやすさ（こ
の場合では蛇腹は短くされるかより強い耐久性を
もつ密封装置を与える）又は改良された圧力性能
を示す。その代わりに、本発明で使用する蛇腹
は、機械的面密封装置のための特殊な要求に従つ
てそれらの改良を最高のものにするように、曲げ
やすさと圧力性能の両方において改良するために
設計できる。 As shown in the examples above, the bellows used in accordance with the present invention exhibits improved bendability (in this case the bellows are shortened) compared to similar conventional bellows of symmetrical construction. provide a more durable seal) or exhibit improved pressure performance. Instead, the bellows used in the present invention are designed to be improved both in bendability and pressure performance, so as to maximize those improvements according to the special requirements for mechanical face sealing devices. Can be designed.

本発明を逸脱せずに種々の変形をなしうる、例
えば密封装置が蛇腹の内側に高圧を受けるような
場合には、ひだの山の曲率半径を逆にする。 Various modifications may be made without departing from the invention, such as reversing the radius of curvature of the pleats if the sealing device is subjected to high pressure inside the bellows.

上記の如く、本発明の一体形成蛇腹の「水圧均
衡直径」は実質的に均一であり、蛇腹と連合して
いる密封面が均衡のとれた密封ができるように設
計しなければならないのに、溶接蛇腹について経
験上分かつている「水圧均衡直径」における変化
のために補正装置をつける必要がある環を保持す
るについては比較的複雑な設計を必要とはしな
い。密封面部材はそれ故上記のように蛇腹１６の
端に押し込みばめしてもよい。上記において、蛇
腹と密封面部材の間に密封を形成するためにＯ−
リングを使用しているが、密封面部材と蛇腹の間
の接合が液が漏れないように接合するに充分なだ
け良好ならば無しで済ますこともできる。しかし
製造公差を調節するために適当な密封剤の層をそ
の間に塗つてもよい。その代わりに、蛇腹の端は
外方向にテーパ付けし、密封面部材の外側表面を
それに合わせてテーパ付けしてもよい。 As noted above, the "hydraulic balance diameter" of the integrally formed bellows of the present invention is substantially uniform and the sealing surfaces associated with the bellows must be designed to provide a balanced seal; There is no need for a relatively complex design for retaining the annulus, which requires compensating devices for changes in the "hydraulic balance diameter" which experience has shown for welded bellows. The sealing face member may therefore be press fit onto the end of the bellows 16 as described above. In the above, O-
Although a ring is used, it can be omitted if the joint between the sealing face member and the bellows is good enough to form a leak-tight joint. However, a layer of a suitable sealant may be applied between them to accommodate manufacturing tolerances. Alternatively, the ends of the bellows may be tapered outwardly and the outer surface of the sealing face member may be tapered accordingly.

そのような型のプレスばめでは、蛇腹部品に関
して密封面部材の軸方向の位置決めをする何らか
の手段が必要である。これは、図に示すように、
密封面部材を蛇腹の最初のひだの壁に接合させる
ことによつて達成される。しかしこの装置では、
密封面部材は蛇腹の最初のひだが曲がらないよう
にし、ひいては蛇腹の全体の曲げやすさを減ら
す。それ故密封面部材を最初のひだの壁から離す
ことが望ましく、この目的のために接合面は蛇腹
の端部に設ける。 Such types of press fits require some means of axial positioning of the sealing face member with respect to the bellows part. This is as shown in the figure.
This is achieved by joining the sealing face member to the wall of the first pleat of the bellows. However, with this device,
The sealing face member prevents the first fold of the bellows from bending, thus reducing the overall bendability of the bellows. It is therefore desirable to space the sealing surface member away from the wall of the first pleat, and for this purpose an abutment surface is provided at the end of the bellows.

上記のプレスばめは炭素のようなもろい材料で
作られた面部材１５にとつては特に適切である。
その代わり、炭素の密封面部材１５は金属の環の
中に保持され、蛇腹はすえ込、ろう付、あるいは
溶接によつてそれに連結してもよい。すえ込は又
蛇腹を直接密封面部材に連結するのに使つてもよ
く、その場合密封面部材は焼結炭化金属あるいは
窒化金属のような堅い材料で作られる。 The press fit described above is particularly suitable for face members 15 made of brittle materials such as carbon.
Alternatively, the carbon sealing face member 15 may be held within a metal ring and the bellows may be connected thereto by swaging, brazing, or welding. Swags may also be used to connect the bellows directly to a sealing face member, in which case the sealing face member is made of a hard material such as sintered metal carbide or metal nitride.

この明細書で用いる「一体形成蛇腹」という語
は一体形成構造のいかなる蛇腹をも意味し、その
ような蛇腹は例えば圧延あるいは吹製のような適
当な形成方法によつて、管状の金属から作られる
のが都合がよい。しかし、蛇腹は例えばポリテト
ロフルオロエチレン類のような硬質プラスチツク
スから作つてもよい。そのような蛇腹は金属製蛇
腹を作るのに使用する方法と似た方法あるいは、
例えば機械加工もしくは適当な直接鋳造のような
他の適当な方法によつて作られる。 As used herein, the term "one-piece bellows" refers to any bellows of one-piece construction, such a bellows being made from tubular metal by any suitable forming method, such as rolling or blowing. It's convenient to be able to do it. However, the bellows may also be made of hard plastics, such as polytetrofluoroethylenes. Such bellows may be made using methods similar to those used to make metal bellows or
For example, it is made by machining or other suitable methods, such as suitable direct casting.

さらに蛇腹は多重構造としてもよく、その場合
には例えば、金属蛇腹の腐食を防ぐための金属蛇
腹の少なくとも一つの表面は非金属で覆う必要が
ある。 Furthermore, the bellows may have a multilayer structure, in which case at least one surface of the metal bellows must be covered with a non-metallic material to prevent corrosion of the metal bellows, for example.

上記の実施態様では、蛇腹のひだの壁が平行で
あり、蛇腹の特性の変化は、ひだの山の間の壁の
構造を変えることによつて達成される。例えば壁
はひだの山の間を凹入する構造とするために連続
して湾曲させてもよい。 In the embodiments described above, the walls of the folds of the bellows are parallel and changes in the properties of the bellows are achieved by changing the structure of the walls between the crests of the folds. For example, the wall may be continuously curved to create a recessed structure between the ridges of the pleats.

【図面の簡単な説明】[Brief explanation of the drawing]

図は、本発明による機械的面密封装置の断面を
図式的に表した図である。 １０：軸、１５：環状密封面部材、１１：ハウ
ジング、１６：一体形成蛇腹、１２：台座、１
７：つば、１３，１８，２０：Ｏ−リング、１
４：密封面。 The figure is a diagrammatic representation of a cross-section of a mechanical surface sealing device according to the invention. 10: shaft, 15: annular sealing surface member, 11: housing, 16: integrally formed bellows, 12: pedestal, 1
7: Brim, 13, 18, 20: O-ring, 1
4: Sealing surface.

Claims (1)

【特許請求の範囲】 １ 相対的に回転可能な一対の機械構成要素１
０，１１の間に密封を形成し、使用の際に圧力差
を受ける機械的面密封装置において、面密封装置
は、該要素の一方１１に液密態様で固着されてい
て密封面を有する第１密封面部材１２と、第１密
封面部材１２の密封面に押しつけられている密封
面１４を有する第２密封面部材１５とよりなり、
第２密封面部材１５は、他の構成要素１０に第２
密封面部材１５を密封させる役目をする曲げやす
く弾力のある一体形成蛇腹１６が、つば１７を介
して他の構成要素１０に固着されており、該蛇腹
１６は、多数のひだを有し、面密封装置の高圧側
（Ｐ）の方に向いているひだの山２１は、面密封
装置の低圧側を向いているひだの山２２よりも曲
率半径が大きい、ことを特徴とする機械的面密封
装置。 ２ 蛇腹１６の高圧側に向いたひだの山２１の曲
率半径の蛇腹１６の低圧側を向いた山２２の曲率
半径に対する比が少なくとも３：２であることを
特徴とする特許請求の範囲第１項の機械的面密封
装置。 ３ 蛇腹１６の高圧側に向いたひだの山２１の曲
率半径の蛇腹１６の低圧側を向いた山２２の曲率
半径に対する比が２：１から６：１の範囲にある
ことを特徴とする特許請求の範囲第１項の機械的
面密封装置。 ４ 蛇腹に圧力が加えられていない時には、蛇腹
のひだの壁が、平行であることを特徴とする特許
請求の範囲第１、２又は３項の機械的面密封装
置。 ５ 蛇腹に圧力が加えられていないときには、蛇
腹１６のひだの壁が湾曲していることを特徴とす
る特許請求の範囲第１、２又は３項の機械的面密
封装置。 ６ 蛇腹１６が金属でできていることを特徴とす
る特許請求の範囲第１、２、３、４又は５項の機
械面密封装置。 ７ 蛇腹１６が硬質プテスチツクス材料でできて
いることを特徴とする特許請求の範囲第１、２、
３、４、５又は６項の機械的面密封装置。 ８ 蛇腹１６が多重構造であることを特徴とする
特許請求の範囲第１、２、３、４、５、６又は７
項の機械的面密封装置。 ９ 第２シール表面部材１５が蛇腹１６の端に押
し込みばめされていることを特徴とする特許請求
の範囲第１、２、３、４、５、６、７又は８項の
機械的面密封装置。 １０ 接合面が蛇腹１６の端部に設けられてお
り、その接合面は蛇腹のひだから離れたところに
あり、第２シール表面部材１５を蛇腹の端部で軸
方向に位置決めするように作用することを特徴と
する特許請求の範囲第９項の機械的面密封装置。 １１ 第２シール表面部材が液密態様で蛇腹１６
に固着されている保持環の中に位置決めされてい
ることを特徴とする特許請求の範囲第１、２、
３、４、５、６、７又は８項の機械的面密封装
置。 １２ 蛇腹１６の端部が保持環にすえ込まれ、ろ
う付けされあるいは溶接されていることを特徴と
する特許請求の範囲第１１項の機械的面密封装
置。 １３ 第２シール表面部材が堅い材料でできてお
り、蛇腹１６の端部がシール表面部材に直接すえ
込まれていることを特徴とする特許請求の範囲第
１、２、３、４、５、６、７、８又は９項の機械
的面密封装置。[Claims] 1. A pair of relatively rotatable mechanical components 1
In a mechanical face sealing device which forms a seal between 0 and 11 and which is subjected to a pressure differential in use, the face seal comprises a second element 11 which is affixed in a fluid-tight manner to one of the elements 11 and has a sealing surface. a second sealing surface member 15 having a sealing surface 14 pressed against the sealing surface of the first sealing surface member 12;
The second sealing surface member 15 is connected to the other component 10 in a second manner.
A pliable, resilient, integrally formed bellows 16 serving to seal the sealing face member 15 is secured to the other component 10 via a collar 17, the bellows 16 having a number of pleats and a surface. Mechanical surface sealing characterized in that the pleat ridges 21 facing towards the high pressure side (P) of the sealing device have a larger radius of curvature than the pleat ridges 22 pointing towards the low pressure side of the surface sealing device. Device. 2. Claim 1, characterized in that the ratio of the radius of curvature of the crests 21 of the folds facing the high-pressure side of the bellows 16 to the radius of curvature of the crests 22 of the bellows 16 facing the low-pressure side is at least 3:2. Mechanical surface sealing device. 3. A patent characterized in that the ratio of the radius of curvature of the ridges 21 of the folds facing the high-pressure side of the bellows 16 to the radius of curvature of the crests 22 of the bellows 16 facing the low-pressure side is in the range of 2:1 to 6:1. A mechanical surface sealing device according to claim 1. 4. A mechanical surface sealing device according to claim 1, 2 or 3, characterized in that the walls of the folds of the bellows are parallel when no pressure is applied to the bellows. 5. A mechanical surface sealing device according to claim 1, 2 or 3, characterized in that the walls of the folds of the bellows (16) are curved when no pressure is applied to the bellows. 6. The mechanical surface sealing device according to claim 1, 2, 3, 4 or 5, wherein the bellows 16 is made of metal. 7. Claims 1, 2, and 3, characterized in that the bellows 16 is made of a hard plastic material.
Mechanical surface sealing device of paragraph 3, 4, 5 or 6. 8. Claims 1, 2, 3, 4, 5, 6, or 7, characterized in that the bellows 16 has a multilayer structure.
Mechanical surface sealing device. 9. Mechanical surface sealing according to claim 1, 2, 3, 4, 5, 6, 7 or 8, characterized in that the second sealing surface member 15 is press-fitted to the end of the bellows 16. Device. 10 an abutment surface is provided at the end of the bellows 16, the abutment surface being remote from the folds of the bellows and operative to axially position the second sealing surface member 15 at the end of the bellows; A mechanical surface sealing device according to claim 9, characterized in that: 11 The second sealing surface member is bellows 16 in a liquid-tight manner.
Claims 1, 2,
Mechanical surface sealing device of paragraph 3, 4, 5, 6, 7 or 8. 12. The mechanical surface sealing device according to claim 11, wherein the end of the bellows 16 is swaged into the retaining ring and is brazed or welded to the retaining ring. 13. Claims 1, 2, 3, 4, 5, characterized in that the second sealing surface member is made of a rigid material, and the ends of the bellows 16 are swaged directly into the sealing surface member. Mechanical surface sealing device of paragraph 6, 7, 8 or 9.
JP56115023A 1980-07-24 1981-07-22 Mechanical surface seal Granted JPS5743060A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB8024235 1980-07-24

Publications (2)

Publication Number Publication Date
JPS5743060A JPS5743060A (en) 1982-03-10
JPS6260581B2 true JPS6260581B2 (en) 1987-12-17

Family

ID=10515003

Family Applications (1)

Application Number Title Priority Date Filing Date
JP56115023A Granted JPS5743060A (en) 1980-07-24 1981-07-22 Mechanical surface seal

Country Status (11)

Country Link
US (1) US4378119A (en)
JP (1) JPS5743060A (en)
AU (1) AU541043B2 (en)
BE (1) BE889705A (en)
CA (1) CA1146989A (en)
CH (1) CH641258A5 (en)
DE (1) DE3129113A1 (en)
FR (1) FR2489464B1 (en)
IN (1) IN155066B (en)
NL (1) NL185237B (en)
SG (1) SG78684G (en)

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Also Published As

Publication number Publication date
FR2489464A1 (en) 1982-03-05
CA1146989A (en) 1983-05-24
FR2489464B1 (en) 1988-08-26
NL8103496A (en) 1982-02-16
DE3129113A1 (en) 1982-05-06
US4378119A (en) 1983-03-29
BE889705A (en) 1981-11-16
NL185237B (en) 1989-09-18
AU541043B2 (en) 1984-12-13
AU7310781A (en) 1982-01-28
SG78684G (en) 1985-04-26
JPS5743060A (en) 1982-03-10
DE3129113C2 (en) 1991-01-10
CH641258A5 (en) 1984-02-15
IN155066B (en) 1984-12-29

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